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WO2018163422A1 - 冷凍サイクル装置 - Google Patents

冷凍サイクル装置 Download PDF

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Publication number
WO2018163422A1
WO2018163422A1 PCT/JP2017/009793 JP2017009793W WO2018163422A1 WO 2018163422 A1 WO2018163422 A1 WO 2018163422A1 JP 2017009793 W JP2017009793 W JP 2017009793W WO 2018163422 A1 WO2018163422 A1 WO 2018163422A1
Authority
WO
WIPO (PCT)
Prior art keywords
mode
refrigerant
pressure
heat exchanger
flow path
Prior art date
Application number
PCT/JP2017/009793
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
悟 梁池
博和 南迫
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2019504282A priority Critical patent/JP6795680B2/ja
Priority to EP17899458.8A priority patent/EP3594592B1/de
Priority to PCT/JP2017/009793 priority patent/WO2018163422A1/ja
Publication of WO2018163422A1 publication Critical patent/WO2018163422A1/ja

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • F25B47/025—Defrosting cycles hot gas defrosting by reversing the cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/029—Control issues
    • F25B2313/0291—Control issues related to the pressure of the indoor unit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/029—Control issues
    • F25B2313/0292—Control issues related to reversing valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0401—Refrigeration circuit bypassing means for the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/26—Problems to be solved characterised by the startup of the refrigeration cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0251—Compressor control by controlling speed with on-off operation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2501—Bypass valves

Definitions

  • the compressor 11 adiabatically compresses a low-pressure gaseous refrigerant (gas refrigerant) and discharges the high-pressure gas refrigerant.
  • the four-way valve 15 connects the discharge port of the compressor 11 and the heat exchanger 12 in the heating mode, and connects the heat exchanger 14 and the suction port of the compressor 11. In the heating mode, the four-way valve 15 forms a flow path so that the refrigerant circulates in the order of the compressor 11, the four-way valve 15, the heat exchanger 12, the expansion valve 13, and the heat exchanger 14.
  • the pressure difference at the start of the defrost mode between the high-pressure side pressure and the low-pressure side pressure is set to the differential pressure at the end of the heating mode while suppressing the amount of refrigerant flowing out of the heat exchanger 12. Can be made smaller.
  • the pressure equalization mode is executed before the defrosting mode, and the differential pressure between the pressure of the high-pressure side refrigerant and the pressure of the low-pressure side refrigerant at the start of the defrosting mode is set to the differential pressure at the end of the heating mode. By making it smaller than this, the amount of refrigerant flowing out of the heat exchanger 12 at the start of the defrosting mode can be suppressed. Therefore, the temperature drop of the heat exchanger 12 at the start of the defrosting mode can be suppressed. As a result, the refrigeration cycle apparatus 1 can be stably operated.
  • FIG. 5 is a flowchart showing a flow of processing performed by the control device 17 of FIG. 1 in the pressure equalization mode. The process shown in FIG. 5 is a process performed in S200 of FIG.
  • the control device 17 stops the compressor 11 in S201 and advances the process to S202.
  • the control device 17 closes the expansion valve 13 in S202 and advances the process to S203.
  • the control device 17 opens the on-off valve 16 in S203 and advances the process to S204.
  • the control device 17 determines whether or not the differential pressure between the discharge pressure and the suction pressure is smaller than the reference differential pressure. When the differential pressure between the discharge pressure and the suction pressure is smaller than the reference differential pressure (YES in S204), the controller 17 has sufficiently reduced the differential pressure between the high-pressure side refrigerant pressure and the low-pressure side refrigerant pressure. The process is returned to the main routine.
  • FIG. 7 is an enlarged view of the vicinity of the connection portion J10 between the flow path RP1 connecting the suction port of the compressor 11 and the four-way valve 15 in FIG. 4 and the flow path RP2 through which the refrigerant from the on-off valve 16 passes.
  • the angle ⁇ 1 formed by the flow paths RP1 and RP2 is larger than 0 degree and smaller than 180 degrees. Therefore, the refrigerant flowing through the flow path RP2 collides with the inner wall of the flow path RP1 at the connection portion J10 between the flow paths RP1 and RP2.
  • the amount of refrigerant per unit time that passes through the on-off valve 16 in the pressure equalization mode decreases. As a result, the amount of refrigerant flowing out of the heat exchanger 12 can be further suppressed in the pressure equalization mode.
  • Embodiment 2 FIG. In Embodiment 1, the case where the on-off valve opened in the pressure equalization mode is closed before the compressor is started in the defrost mode has been described. In the second embodiment, a case where the on-off valve is closed after starting the compressor in the defrosting mode will be described.
  • the compressor is operated with the on-off valve opened for a while from the start of the defrosting mode. While the release valve is open, a part of the refrigerant discharged from the compressor is returned to the compressor inlet via the on-off valve.
  • the refrigerant from the heat exchanger functioning as the condenser in the heating mode is less likely to be sucked into the compressor by the amount of the refrigerant returned to the compressor inlet through the on-off valve. As a result, the amount of refrigerant flowing out from the heat exchanger at the start of the defrost mode can be further suppressed.
  • FIG. 9 is a flowchart showing a flow of processing performed by the control device 17 of FIG. 8 in the defrosting mode.
  • the control device 17 advances the process to S ⁇ b> 312.
  • the control device 17 opens the expansion valve 13 to an appropriate opening degree in S312, and advances the process to S313.
  • the control device 17 activates the compressor 11 in S313 and advances the process to S314.
  • the control device 17 determines whether or not the defrost termination condition is satisfied in S314. When the defrost termination condition is satisfied (YES in S314), control device 17 causes the process to proceed to S315.
  • the controller 17 determines whether or not the on-off valve 16 is open in S315.
  • control device 17 When on-off valve 16 is closed (NO in S315), control device 17 returns the process to the main routine. If the on-off valve 16 is open (YES in S315), the control device 17 closes the on-off valve 16 in S316, and then returns the process to the main routine.
  • control device 17 advances the process to S317.
  • S317 the control device 17 determines whether or not the suction pressure exceeds the reference pressure. If the suction pressure exceeds the reference pressure (YES in S317), the controller 17 determines that the suction pressure has increased sufficiently, closes the on-off valve 16 in S319, waits for a certain time in S320, and then performs the process in S314. Return to. If the suction pressure is equal to or lower than the reference pressure (NO in S317), control device 17 advances the process to S318. The control device 17 determines whether or not a reference time has elapsed since the compressor 11 was started in S318.
  • the control device If the reference time has elapsed since the start of the compressor 11 (YES in S318), it is determined that a sufficient time has passed to increase the suction pressure, and the on-off valve 16 is closed in S319, and the predetermined time is determined in S320. After waiting, the process returns to S314. If the reference time has not elapsed since the compressor 11 was started (NO in S318), the control device returns the process to S314.
  • the reference pressure in S317 and the reference time in S318 can be appropriately calculated by actual machine experiments or simulations.
  • the decrease can be suppressed.
  • the refrigeration cycle apparatus can be stably operated.
  • Embodiment 3 FIG.
  • the case where the pressure equalization mode is performed next to the heating mode when the defrosting start condition is satisfied has been described.
  • the pump down mode the amount of refrigerant in the heat exchanger functioning as a condenser in the heating mode is increased.
  • the amount of refrigerant in the heat exchanger at the start of the pressure equalization mode is increased as compared to the first embodiment. Therefore, the temperature fall at the time of the defrost mode start of the said heat exchanger can further be suppressed. As a result, the refrigeration cycle apparatus can be operated more stably.
  • FIG. 10 is a flowchart showing a flow of processing in which the control device of the refrigeration cycle apparatus according to Embodiment 3 switches the operation mode of the refrigeration cycle apparatus.
  • the control device executes the pump down mode in S100. Thereafter, as in the first embodiment, the control device executes the pressure equalization mode in S200 and executes the defrosting mode in S300.
  • the control device switches the operation mode in the order of the heating mode, the pump down mode, the pressure equalization mode, and the defrosting mode.
  • FIG. 11 is a diagram illustrating a functional configuration of the refrigeration cycle apparatus 3 according to Embodiment 3 and a refrigerant flow in the pump down mode.
  • the control device 17 operates the compressor 11, closes the expansion valve 13, and closes the on-off valve 16.
  • the four-way valve 15 maintains the connection between the discharge port of the compressor 11 and the heat exchanger 12 and the connection between the heat exchanger 14 and the suction port of the compressor 11. Since the compressor 11 is operating and the expansion valve 13 is closed, the refrigerant discharged from the compressor 11 is stored in the heat exchanger 12. While the pump-down mode is performed, the amount of refrigerant in the heat exchanger 12 increases.
  • the refrigerant amount in the heat exchanger 12 at the start of the pressure equalization mode is increased as compared with the first embodiment in which the pump down mode is not performed.
  • the amount of refrigerant remaining in the heat exchanger 12 is increased from that in the first embodiment. Therefore, the temperature drop of the heat exchanger 12 is reduced from that in the first embodiment. Can also be suppressed.
  • FIG. 12 is a flowchart showing a flow of processing performed by the control device 17 of FIG. 11 in the pump down mode. The process shown in FIG. 12 is a process performed in S100 of FIG.
  • the pressure equalization mode (S200) may be executed without performing the pump down mode.
  • the interruption time of the heating mode can be shortened.
  • Modification 1 and Modification 2 by performing the pressure equalization mode before the defrost mode, as a condenser in the heating mode at the start of the defrost mode. It is possible to suppress the temperature drop of the functioning heat exchanger. As a result, the refrigeration cycle apparatus can be stably operated.
  • the heat exchange functioning as the condenser in the heating mode at the start of the defrost mode is performed by executing the pressure equalization mode before the defrost mode.
  • the temperature drop of the vessel can be suppressed.
  • the refrigeration cycle apparatus can be stably operated.
  • the flow path switching device can operate when the differential pressure between the pressure of the high-pressure side refrigerant and the pressure of the low-pressure side refrigerant is smaller than the reference differential pressure. It is possible to prevent the situation of being unable to do so. As a result, the refrigeration cycle apparatus can be operated more stably.
  • Embodiment 5 a case where a gas-liquid separator is connected between the on-off valve and the suction port of the compressor will be described.
  • the refrigerant flowing out in the pressure equalization mode from the heat exchanger functioning as a condenser in the heating mode is stored in the gas-liquid separator in the pressure equalization mode.
  • the refrigerant from the gas-liquid separator is also added, so that the outflow from the heat exchanger at the start of the defrosting mode The amount of refrigerant to be performed can be suppressed as compared with the first embodiment.
  • the heat exchanger in the pressure equalizing mode The refrigerant from is stored in the gas-liquid separator. Since the refrigerant from the gas-liquid separator is also added to the refrigerant sucked into the compressor at the start of the defrosting mode, the temperature drop of the heat exchanger functioning as a condenser in the heating mode is reduced to the same level as in the first embodiment. Can be suppressed.
  • the time required for the pressure equalization mode can be reduced as compared with the first embodiment by making the flow path resistance of the on-off valve smaller than that of the first embodiment. As a result, the interruption time of the heating operation can be shortened.
  • FIG. 18 is a diagram illustrating a functional configuration of the refrigeration cycle apparatus 5 according to Embodiment 5 and a refrigerant flow in the pressure equalization mode.
  • the on-off valve 16 of the refrigeration cycle apparatus 1 shown in FIG. 4 is replaced with an on-off valve 165.
  • the channel resistance of the on-off valve 165 when the on-off valve 165 is open is larger than the channel resistance of the four-way valve 15 and smaller than the channel resistance of the on-off valve 16 when the on-off valve 16 is open.
  • the refrigeration cycle apparatus 5 further includes a gas-liquid separator 50 in addition to the configuration of the refrigeration cycle apparatus 1 shown in FIG.
  • the refrigerant that has flowed out of the heat exchanger 12 in the pressure equalization mode passes through the on-off valve 16 and is then stored in the gas-liquid separator 50.
  • the liquid refrigerant stored in the gas-liquid separator 50 is discharged from the discharge port LS1, and merges with the refrigerant toward the heat exchanger 14 at the junction J2.
  • the refrigerant from the heat exchanger that has functioned as a condenser in the heating mode is stored in the gas-liquid separator, thereby functioning as a condenser in the heating mode.
  • the amount of refrigerant flowing out from the heat exchanger at the start of the defrosting mode can be suppressed.
  • the flow path resistance of the on-off valve can be made smaller than that in the first embodiment, the time required for the pressure equalization mode can be made smaller than that in the first embodiment.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
PCT/JP2017/009793 2017-03-10 2017-03-10 冷凍サイクル装置 WO2018163422A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP2019504282A JP6795680B2 (ja) 2017-03-10 2017-03-10 冷凍サイクル装置
EP17899458.8A EP3594592B1 (de) 2017-03-10 2017-03-10 Kältekreislaufvorrichtung
PCT/JP2017/009793 WO2018163422A1 (ja) 2017-03-10 2017-03-10 冷凍サイクル装置

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2017/009793 WO2018163422A1 (ja) 2017-03-10 2017-03-10 冷凍サイクル装置

Publications (1)

Publication Number Publication Date
WO2018163422A1 true WO2018163422A1 (ja) 2018-09-13

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ID=63448722

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Application Number Title Priority Date Filing Date
PCT/JP2017/009793 WO2018163422A1 (ja) 2017-03-10 2017-03-10 冷凍サイクル装置

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EP (1) EP3594592B1 (de)
JP (1) JP6795680B2 (de)
WO (1) WO2018163422A1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20210164712A1 (en) * 2018-07-25 2021-06-03 Guangdong Meizhi Compressor Co., Ltd. Compressor and refrigeration device

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58129471U (ja) * 1982-02-25 1983-09-01 ゼネラル・エアコン株式会社 除霜制御装置
JPH0673667U (ja) * 1993-03-17 1994-10-18 ヤンマーディーゼル株式会社 多室空調型ヒートポンプシステムにおける均圧装置
JP2002122361A (ja) * 2000-10-13 2002-04-26 Sanyo Electric Co Ltd 冷凍装置、及びこの冷凍装置を用いた空気調和装置
JP2005283041A (ja) * 2004-03-31 2005-10-13 Daikin Ind Ltd 調湿装置
JP2011174662A (ja) 2010-02-24 2011-09-08 Mitsubishi Heavy Ind Ltd 空気熱源ヒートポンプ給湯・空調装置
WO2012042573A1 (ja) * 2010-09-30 2012-04-05 三菱電機株式会社 空気調和装置
JP2015068611A (ja) * 2013-09-30 2015-04-13 ダイキン工業株式会社 空気調和装置

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10047983B2 (en) * 2013-12-11 2018-08-14 Trane International Inc. Reduced power heat pump starting procedure
JP6582236B2 (ja) * 2015-06-11 2019-10-02 パナソニックＩｐマネジメント株式会社 冷凍サイクル装置

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58129471U (ja) * 1982-02-25 1983-09-01 ゼネラル・エアコン株式会社 除霜制御装置
JPH0673667U (ja) * 1993-03-17 1994-10-18 ヤンマーディーゼル株式会社 多室空調型ヒートポンプシステムにおける均圧装置
JP2002122361A (ja) * 2000-10-13 2002-04-26 Sanyo Electric Co Ltd 冷凍装置、及びこの冷凍装置を用いた空気調和装置
JP2005283041A (ja) * 2004-03-31 2005-10-13 Daikin Ind Ltd 調湿装置
JP2011174662A (ja) 2010-02-24 2011-09-08 Mitsubishi Heavy Ind Ltd 空気熱源ヒートポンプ給湯・空調装置
WO2012042573A1 (ja) * 2010-09-30 2012-04-05 三菱電機株式会社 空気調和装置
JP2015068611A (ja) * 2013-09-30 2015-04-13 ダイキン工業株式会社 空気調和装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3594592A4

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20210164712A1 (en) * 2018-07-25 2021-06-03 Guangdong Meizhi Compressor Co., Ltd. Compressor and refrigeration device
US11933526B2 (en) * 2018-07-25 2024-03-19 Guangdong Meizhi Compressor Co., Ltd. Compressor and refrigeration device

Also Published As

Publication number Publication date
EP3594592B1 (de) 2023-05-10
JP6795680B2 (ja) 2020-12-02
JPWO2018163422A1 (ja) 2019-11-07
EP3594592A1 (de) 2020-01-15
EP3594592A4 (de) 2020-02-26

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